WO2017221522A1 - Mécanisme d'engrenage pour horloge - Google Patents

Mécanisme d'engrenage pour horloge Download PDF

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Publication number
WO2017221522A1
WO2017221522A1 PCT/JP2017/014822 JP2017014822W WO2017221522A1 WO 2017221522 A1 WO2017221522 A1 WO 2017221522A1 JP 2017014822 W JP2017014822 W JP 2017014822W WO 2017221522 A1 WO2017221522 A1 WO 2017221522A1
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WO
WIPO (PCT)
Prior art keywords
gear
pinion
pressure angle
torque
teeth
Prior art date
Application number
PCT/JP2017/014822
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English (en)
Japanese (ja)
Inventor
福田　匡広
新平 深谷
Original Assignee
シチズン時計株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by シチズン時計株式会社 filed Critical シチズン時計株式会社
Priority to PCT/JP2017/022552 priority Critical patent/WO2017221897A1/fr
Priority to US16/312,950 priority patent/US10895844B2/en
Priority to EP17815365.6A priority patent/EP3447589B1/fr
Priority to CN201780031446.2A priority patent/CN109154793B/zh
Priority to JP2018524089A priority patent/JP6876694B2/ja
Publication of WO2017221522A1 publication Critical patent/WO2017221522A1/fr

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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots
    • G04B13/027—Wheels; Pinions; Spindles; Pivots planar toothing: shape and design
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/0806—Involute profile
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots

Definitions

  • the present invention relates to a train wheel mechanism of a watch.
  • the timepiece is equipped with a gear train mechanism in which a plurality of gear devices mesh with each other in order to transmit the power generated by the power source by increasing or decreasing the speed.
  • a gear device has a gear having a large diameter and a large number of teeth, and a pinion having a small diameter and a small number of teeth, which are fixed to a common shaft (true). The gear of one gear unit is engaged.
  • the gears and kana of these gear devices include, for example, those having an involute curve outline tooth profile and those having an arc curve outline tooth profile.
  • the present invention has been made in view of the above circumstances, and suppresses fluctuations in transmitted torque, which is composed of a tooth-shaped gear having an involute curve outline that is easy to manufacture, and a cane meshing with the gear, and is stable.
  • An object of the present invention is to provide a train wheel mechanism for a timepiece that operates in the same manner.
  • the present invention comprises a gear having a tooth profile tooth having an involute curve contour, and a pinion having a tooth that meshes with the tooth of the gear and receives torque, and at least a first half of a meshing period in which the gear and the pinion mesh with each other.
  • the gear train mechanism of the watch is such that the torque transmitted from the gear to the pinion is substantially constant.
  • the train wheel mechanism of the timepiece of the present invention is composed of a tooth-shaped gear having an involute curve outline that is easy to manufacture and a pinion that meshes with the gear, and suppresses fluctuations in transmitted torque and stabilizes it. Can work.
  • FIG. 5 is a schematic diagram showing a train wheel mechanism in a portable timepiece (for example, a wristwatch) according to an embodiment of the present invention, in which contact (close meshing) between the driving-side gear teeth and the driven-side kana teeth starts.
  • a train wheel mechanism of a portable timepiece for example, a wristwatch
  • FIG. 5 shows a state (No. 1) from the start of distant meshing to the end of distant meshing.
  • 3 is a graph showing a torque transmission rate corresponding to FIG. 2 when the pressure angle difference is changed to 1.5 [degrees], 2 [degrees], and 3 [degrees] in the gear train mechanism of the present embodiment.
  • DELTA shift amount
  • 6 is a graph showing a torque transmission rate corresponding to FIG. 5 when the pressure angle difference is changed to ⁇ 2 degrees, ⁇ 1 degrees, and 0 degrees in the gear train mechanism of the second embodiment. .
  • FIG. 1A is a schematic diagram showing a train wheel mechanism 1 in a portable timepiece (for example, a wristwatch) according to an embodiment of the present invention, in which a tooth 11 of a driving gear 10 and a tooth 21 of a follower kana 20 are illustrated. The state where contact has started is shown.
  • the illustrated train wheel mechanism 1 includes, for example, a gear 10 for a second wheel and a pinion 20 for a third wheel.
  • the gear 10 and the pinion 20 are engaged with each other, and torque is transmitted from the gear 10 to the pinion 20 through an engagement point T where the gear 10 and the pinion 20 are in contact with each other.
  • the contour 12 of the tooth profile of each tooth 11 is formed by an involute curve having a pressure angle ⁇ 2 of 22 degrees. This pressure angle is defined by the Japanese Industrial Standard (JIS B 0102), and is the angle formed by the radial line and the tangent to the tooth profile at one point on the tooth surface.
  • JIS B 0102 Japanese Industrial Standard
  • the tooth profile contour 22 of each tooth 21 meshes with a virtual gear corresponding to an involute curve of a pressure angle ⁇ 1 (for example, 23.5 [degrees]) larger than the pressure angle ⁇ 2 of the tooth 11. It is formed by a constant torque curve in which the torque transmitted from the virtual gear to the pinion 20 is substantially constant during the meshing period from the start of meshing with the 20 teeth 21 to the completion of meshing.
  • the torque transmitted from the gear 10 to the pinion 20 is substantially constant in at least a partial range (for example, the close-engagement range) of the first half of the engagement period between the teeth 11 of the gear 10 and the teeth 21 of the pinion 20.
  • the distance (interaxial distance) between the rotation center of the gear 10 and the rotation center of the pinion 20 is, for example, 3 [mm].
  • FIGS. 1B and 1C show the close meshing range in the first half of the meshing period described above including FIG. 1A. It is shown in chronological order. That is, FIG. 1A shows a state where meshing starts, FIG. 1B shows a state between the start of meshing and the end of close meshing, and FIG.
  • the close engagement is between the tip circle and the pitch point of the driven (driven) gear (can 20 in the present embodiment) defined by the Japanese Industrial Standard (JIS B 0102). It is the state of the range on the locus of the contact point, and the disengagement (recess contact) is the contact between the pitch point and the tooth tip circle of the drive gear as defined in Japanese Industrial Standard (JIS B 0102) It is the state of the range on the locus of points.
  • FIGS. 1C, 1D, 1E, and 1F are also schematic diagrams showing the train wheel mechanism 1.
  • FIGS. 1C, 1D, 1E, and 1F are time-series in the range of distant meshing in the latter half of the meshing period described above. It is shown in order. That is, FIG. 1C is the end of the close meshing and the start of the distant meshing, FIGS. 1D and 1E are the states from the start of the distant meshing to the end of the distant meshing (part 1 and 2), and FIG. 1F is the far meshing. Each end state is shown.
  • FIG. 1D shows a state between FIG. 1C and FIG. 1E in time series.
  • FIG. 2 is a graph showing the torque transmission efficiency from the gear 10 to the pinion 20 when the gear 10 and the pinion 20 are engaged by the gear train mechanism 1 of the watch of the present embodiment.
  • 1) is the meshing state shown in FIG. 1A
  • (2) is the meshing state shown in FIG. 1B
  • (3) is the meshing state shown in FIG. 1C
  • (4) is the meshing state shown in FIG. 1D
  • (5) Is the meshing state shown in FIG. 1E
  • (6) is the rotation angle (horizontal axis) and torque transmission efficiency (vertical axis) of the gear 10 corresponding to the meshing state shown in FIG. 1F.
  • the train wheel mechanism 1 of the timepiece according to the present embodiment has a close meshing range (about 1.7 [degrees] as the rotation angle of the gear 10) shown in FIGS. 1A, 1B, and 1C. Range), the torque transmission rate of the torque transmitted from the gear 10 to the pinion 20 is substantially constant (0.93 to 0.94).
  • the train wheel mechanism 1 of the timepiece has a disengagement range shown in FIGS. 1D, 1E, and 1F after passing FIG. 1C (a range of about 3.3 [degrees] as the rotation angle of the gear 10).
  • the torque transmission rate of the torque transmitted from the gear 10 to the pinion 20 increases from the close meshing range to exceed 0.98, and then reaches about 0.93 to 0.94 in the close meshing range. Decrease.
  • FIG. 3 is a graph showing a torque transmission rate (solid line) of the train wheel mechanism 1 of the timepiece of the present embodiment and a torque transmission rate (broken line) of a conventional train wheel mechanism of the timepiece to which the present invention is not applied.
  • the torque transmission rate of the train wheel mechanism 1 of the watch of the present embodiment indicated by the solid line is the same as that shown in FIG. 2, and the torque transmission rate is the minimum value T MIN and the maximum value T MAX . .
  • the gear has a tooth profile with an involute curve contour
  • the kana has a tooth profile with a so-called ETA's unique contour (not a constant torque curve contour).
  • T MIN of torque transmission rate is slightly larger than 0.91, and this value is smaller than the minimum value T MIN of torque transmission rate in the wheel train mechanism 1 of the present embodiment.
  • the maximum value T MAX of the torque transmission rate in this general train wheel mechanism is substantially the same as the maximum value T MAX of the torque transmission rate in the wheel train mechanism 1 of the present embodiment.
  • the torque transmission rate is substantially constant with a width of 0.01 or less in the range of close engagement during the period in which the gear 10 and the pinion 20 are engaged.
  • the minimum value of the torque transmission rate of the gear train mechanism 1 is larger than the minimum value of the torque transmission rate in the general gear train mechanism to which the present invention is not applied, as indicated by the broken line in FIG. Therefore, the train wheel mechanism 1 of the timepiece of the present embodiment is more stable than the conventional general train wheel mechanism of the timepiece, in which the torque fluctuation that is the difference between the maximum value and the minimum value of the torque transmission rate is suppressed. Operate.
  • the kana 20 has eight teeth 21, but the number Z of the teeth 21 of the kana 20 is not limited to eight, but 7 to 15 It may be in the range.
  • the tooth profile contour 22 of the tooth 21 of the pinion 20 is formed with a constant torque curve in the meshing period meshed with a virtual gear having a large pressure angle ⁇ 1, as described above, the number Z of teeth 21 of the pinion 20 If the number Z is 6 or less, the meshing with the gear 10 is not appropriate. On the other hand, if the number Z is 16 or more, the torque fluctuation does not become a big problem, whereas the number Z is 7, 8, 9 , 10, 11, 12, 13, 14, and 15 have a great effect of suppressing torque fluctuation while realizing proper meshing.
  • the number Z of teeth 21 of the pinion 20 of the train wheel mechanism 1 is more preferably in the range of 7 to 10, and in this case, the effect of suppressing torque fluctuation is greater.
  • FIG. 4 is a graph showing the correspondence between the number of teeth Z of the kana 20 and the pressure angle difference ⁇ .
  • the pressure angle difference ⁇ forms the involute curve pressure angle ⁇ 2 that forms the tooth profile contour 12 of the tooth 11 of the gear 10 with which the pinion 20 actually meshes and the tooth shape contour 22 of the tooth 21 of the pinion 20.
  • a difference ⁇ ( ⁇ 1 ⁇ 2) from the pressure angle ⁇ 1 in the involute curve of the virtual gear used for calculating the constant torque curve.
  • ⁇ is preferably larger than ⁇ (Z / 2) +5 ( ⁇ (Z / 2) +5 ⁇ ).
  • the pressure angle difference ⁇ is not larger than ⁇ (Z / 2) +5, the tooth tip of the pinion 20 may come into contact with the tooth bottom of the gear 10, and the pressure angle difference ⁇ is ⁇ (Z / 2). If it is greater than +5, there is no fear.
  • the difference ⁇ is preferably smaller than ⁇ (Z / 2) +8 ( ⁇ ⁇ (Z / 2) +8).
  • ⁇ (Z / 2) +8 As the pressure angle difference ⁇ increases, the torque transmission rate that is substantially constant in the close engagement range decreases, and the torque transmission rate that is the maximum in the distant engagement range decreases.
  • the torque fluctuation which is a difference in the overall torque transmission rate, increases. Therefore, when the pressure angle difference ⁇ is not smaller than ⁇ (Z / 2) +8, the effect of suppressing torque fluctuation is reduced, but when the pressure angle difference ⁇ is smaller than ⁇ (Z / 2) +8. Can sufficiently suppress torque fluctuations.
  • the range of +7 is more preferable, and in this range ( ⁇ ⁇ (Z / 2) +7), torque fluctuation can be further suppressed.
  • the effect of suppressing the torque fluctuation is greater than that in the case where the difference ⁇ is less than 4.0.
  • FIG. 5 shows a difference in pressure angle ⁇ of 1.5 [degrees] in the gear train mechanism 1 according to the present embodiment (for example, the number of teeth Z of the pinion 20 is 8 and the number of teeth of the meshing gear 10 is 72). It is a graph which shows the torque transmission rate equivalent to FIG. 2 when it changes with 2 [degrees] and 3 [degrees].
  • the pressure angle difference ⁇ 1.5 [degrees]
  • the train wheel mechanism 1 of the above-described embodiment which is the same as the graph shown in FIG.
  • the pressure angle difference ⁇ 2 [degrees]
  • the involute curve that defines the outline of the tooth profile is not limited to the pressure angle ⁇ 2 of 22 [degrees], and the pressure angle ⁇ 2 is 18 [degrees], 19 [degrees], 20 [other than 22 [degrees]. [Degree], 21 [degree], 23 [degree], 24 [degree], 25 [degree], and the like.
  • the pressure angles ⁇ 1 and ⁇ 2 may be angles including decimal numbers, such as 22.5 [degrees] and 23.4 [degrees].
  • FIG. 6 shows the torque when the inter-axis distance between the gear 10 and the pinion 20 in the train wheel mechanism 1 of the present embodiment is changed by a deviation amount ⁇ a [ ⁇ m] with respect to the regular 3 [mm].
  • the minimum torque transmission rate in the torque transmission rate range is larger than that in the case of the normal shaft distance, and the maximum torque transmission rate in the non-constant torque transmission range is smaller than that in the case of the normal shaft distance. The fluctuation is suppressed compared to the case of the normal inter-axis distance.
  • the minimum torque transmission rate in the constant torque transmission rate range becomes smaller than that in the case of the normal shaft distance
  • the maximum torque transmission rate in the non-constant torque transmission rate range becomes larger than that in the case of the normal shaft distance.
  • the torque fluctuation is larger than that in the case of a normal inter-axis distance.
  • the train wheel mechanism 1 of the timepiece according to the present embodiment has the conventional general timepiece shown by the broken line in FIG. 3 in the range where the shift amount ⁇ a of the inter-axis distance is ⁇ 20 [ ⁇ m] to 20 [ ⁇ m]. Compared with the gear train mechanism, torque fluctuation is sufficiently suppressed.
  • the train wheel mechanism of the timepiece of the present embodiment is a combination of the second wheel gear 10 and the third wheel pinion 20
  • the watch wheel train mechanism according to the present invention is not limited to these combinations. In other words, it may be a combination of the third wheel gear and the fourth wheel kana, a combination of the fourth wheel gear and the escape wheel kana, a combination of the barrel and the second wheel kana, Furthermore, it may be a combination of other gears.
  • FIG. 7 is a schematic diagram for explaining a specific method for setting the outline 22 of the tooth profile of the tooth 21 of the kana 20.
  • a hypothetical gear 10 ′ having a pressure angle ⁇ 1 larger than the pressure angle of the gear 10 that actually meshes with the pinion 20 is assumed.
  • the rotation center of the virtual gear 10 ' is O2
  • the rotation center of the pinion 20 is O1
  • the engagement point between the pinion 20 and the virtual gear 10' is T
  • the pinion 20 and the virtual gear 10 'at the engagement point T Let P be the intersection of the normal line (common normal line) L2 of the common tangent line L1 of the tooth profile and the straight line L3 connecting the rotation centers O1 and O2, and let the friction angle be ⁇ .
  • the intersection point of the straight line L4 and the straight line L3 inclined by the friction angle ⁇ from the common normal line L2 is Q
  • the angle formed by the straight line L3 and the straight line L4 is ⁇
  • the intersections with the perpendiculars L5 and L6 drawn down are denoted by a1 and a2.
  • the length from the rotation center O1 to the intersection Q is R1
  • the length from the rotation center O2 to the intersection Q is R2
  • the length from the rotation center O1 to the intersection a1 is P1
  • the length from the rotation center O2 to the intersection a2 is Let P2.
  • the length R1 and the length R2 need only be constant.
  • a straight line L7 connecting the intersection K1 of the circle E1 with the radius R1 centered on the rotation center O1 and the tooth profile curve F1 set temporarily and the rotation center O1 is used as a reference line, and the reference line L7 and the common tangent L1.
  • a reference line is a straight line L8 connecting the intersection K2 of the circle E2 having a radius R2 centered on the rotation center O2 with the tooth profile curve F2 and the rotation center O2, and the reference line L8
  • the tooth profile curves F1 and F2 can be represented by tangential polar coordinates (P1, ⁇ 1) and tangential polar coordinates (P2, ⁇ 2), respectively.
  • the tangential polar coordinates (P1, ⁇ 1) of the tooth profile curve F1 as a constant torque curve with respect to the involute curve are calculated based on the tangential polar coordinates (P2, ⁇ 2).
  • (alpha) is pressure angle (alpha) 1 of the virtual gearwheel 10 'mentioned above.
  • the tooth profile curve F2 is obtained by the equations (1) to (7). Specifically, polar coordinates (r, ⁇ ) corresponding to the locus of the meshing point T are obtained using the equations (1), (3), (6), and (7), and the obtained values are represented by the equation (2). ), (4), and (5) to obtain tangential polar coordinates (P1, ⁇ 1).
  • the constant term c in equation (9) is obtained by substituting the initial value ⁇ for ⁇ 1 and the initial value ( ⁇ / 2 ⁇ ) for ⁇ .
  • the tangential polar coordinates that define the constant torque curve (tooth profile curve F1) that is the tooth profile of the kana 20 corresponding to the involute curve (tooth profile curve F2) that is the tooth profile of the gear 10 that is defined by the tangential polar coordinates (P2, ⁇ 2). (P1, ⁇ 1) is obtained.
  • the torque transmitted from the gear 10 with which the kana 20 actually meshes is substantially constant in the range of at least a part of the first half of the meshing period.
  • the tooth profile contour 22 of the tooth 21 of the pinion 20 meshes with the virtual gear 10 'corresponding to the involute curve of the pressure angle ⁇ 1 smaller than the pressure angle ⁇ 2 of the tooth 11. It is formed by a constant torque curve in which the torque transmitted from the virtual gear 10 'to the pin 20 is substantially constant during the meshing period from when the virtual gear 10' and the teeth 21 of the pin 20 start to mesh. May be.
  • the train wheel mechanism 1 configured as described above can be the second embodiment (embodiment 2) of the train wheel function according to the present invention.
  • the number Z of teeth 21 of the kana 20 may be in the range of 11 to 20, for example.
  • the number Z of teeth 21 is 11, In the case of 12, 13, 14, 15, 16, 17, 18, 19, and 20, the effect of suppressing torque fluctuation is large while realizing proper meshing.
  • the number Z of teeth 21 of the kana 20 is particularly preferably in the range of 16-20.
  • the pressure angle difference ⁇ is preferably larger than ⁇ (Z / 2) +5 ( ⁇ (Z / 2) +5 ⁇ ).
  • the pressure angle difference ⁇ is preferably smaller than ⁇ (Z / 2) +8 ( ⁇ ⁇ (Z / 2) +8).
  • ⁇ (Z / 2) +8 As the pressure angle difference ⁇ increases (since ⁇ is a negative number, increasing ⁇ is equivalent to ⁇ approaching 0), the torque transmission rate that becomes substantially constant in the range of close engagement is As the substantially constant value decreases, the maximum torque transmission rate value in the distant meshing range increases and torque fluctuation increases. Therefore, when the pressure angle difference ⁇ is not smaller than ⁇ (Z / 2) +8, the effect of suppressing torque fluctuation is reduced, but when the pressure angle difference ⁇ is smaller than ⁇ (Z / 2) +8. Can sufficiently suppress torque fluctuations.
  • an involute curve of the virtual gear 10 ′ used to calculate a constant torque curve that forms the tooth profile contour 22 of the pinion 21 of the pinion 20 is greater than ⁇ 3.5 and less than ⁇ 0.5 (preferably less than ⁇ 1.5).
  • ⁇ the difference between the pressure angle ⁇ 1 and the pressure angle ⁇ 2 of the gear 10 is greater than ⁇ 3.5 and less than ⁇ 0.5 (preferably less than ⁇ 1.5).
  • the tooth tip of the pinion 20 contacts a portion unnecessary for torque transmission (such as the tooth bottom of the gear 10), and the torque transmitted from the gear 10 to the pinion 20 is substantially within at least a part of the first half of the meshing period.
  • a constant train wheel part can be obtained.
  • the effect of suppressing torque fluctuation is greater than that in which the difference ⁇ is less than ⁇ 0.5.
  • FIG. 8 shows a difference in pressure angle ⁇ of 0 [degrees], ⁇ in the gear train mechanism 1 of the second embodiment (for example, the number of teeth Z of the pinion 20 is 109 and the number of teeth of the meshing gear 10 is 109).
  • 6 is a graph showing a torque transmission rate corresponding to FIG. 5 when it is changed to 1 [degree] and ⁇ 2 [degree].
  • the pressure angle difference ⁇ is ⁇ 1 [degree]
  • the wheel train mechanism of the second embodiment includes a combination of the second wheel gear 10 and the third wheel pinion 20, a combination of the third wheel gear and the fourth wheel pinion, and the fourth wheel gear. It may be a combination of a pinion wheel and a combination of a barrel wheel and a second wheel pinion, and may be a combination of other gears.
  • the gear train mechanism 1 of the first embodiment described above describes the pinion 20 having the teeth 21 having the contour shape of the pressure angle ⁇ 1 ( ⁇ becomes positive) larger than the pressure angle ⁇ 2 of the teeth of the gear 10 to be meshed, A preferable value for the number of teeth Z of the kana 20 was set to 7 to 15.
  • the train wheel mechanism 1 according to the second embodiment describes the pinion 20 having the teeth 21 having the contour shape with the pressure angle ⁇ 1 ( ⁇ becomes negative) smaller than the pressure angle ⁇ 2 of the teeth of the gear 10 to be engaged.
  • a preferable value for the number of teeth Z of the kana 20 was set to 11-20.
  • the pinion 20 having the number of teeth Z of 7 to 10 has a pressure angle ⁇ 1 ( ⁇ is positive) greater than the pressure angle ⁇ 2 of the teeth of the gear 10 to be meshed.
  • the pinion 20 having the number of teeth Z of 16 to 20 can have a contour shape having a pressure angle ⁇ 1 ( ⁇ becomes negative) smaller than the pressure angle ⁇ 2 of the teeth of the gear 10 to be meshed.
  • the pinion 20 having the number of teeth Z of 11 to 15 has a contour with a pressure angle ⁇ 1 ( ⁇ is positive) larger than the pressure angle ⁇ 2 of the teeth of the gear 10 to be meshed.
  • It may be a shape or a contour shape with a small pressure angle ⁇ 1 ( ⁇ is negative), but more preferably a pressure angle ⁇ 1 (smaller than the pressure angle ⁇ 2 of the gear teeth to be meshed.
  • the contour shape of ⁇ becomes negative.
  • train wheel mechanism 1 of each embodiment and each modification mentioned above is only a preferable example, and the technical scope of the train wheel mechanism according to the present invention is not limited to these each embodiment and each modification.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)

Abstract

L'invention concerne un mécanisme d'engrenage pour horloge qui est configuré par une roue à forme de dents possédant un contour en courbe involutive de fabrication facile, et un pignon s'engageant avec cette roue, et qui est destiné à supprimer la variation d'un couple transmis. Le mécanisme d'engrenage pour horloge (1) de l'invention est équipé : de la roue (10) qui possède des dents (11) présentant une forme de contour en courbe involutive ; et d'un pignon (20) qui s'engage avec les dents (11) de la roue (10), et qui possède des dents (21) recevant le couple. Dans au moins une partie d'une plage de la première moitié d'une période d'engagement au cours de laquelle la roue (10) et le pignon (20) s'engagent, le couple transmis de la roue (10) au pignon (20) est sensiblement constant.
PCT/JP2017/014822 2016-06-23 2017-04-11 Mécanisme d'engrenage pour horloge WO2017221522A1 (fr)

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Application Number Priority Date Filing Date Title
PCT/JP2017/022552 WO2017221897A1 (fr) 2016-06-23 2017-06-19 Mécanisme d'engrenage pour horloge
US16/312,950 US10895844B2 (en) 2016-06-23 2017-06-19 Gear train mechanism of timepiece
EP17815365.6A EP3447589B1 (fr) 2016-06-23 2017-06-19 Mécanisme d'engrenage pour horloge
CN201780031446.2A CN109154793B (zh) 2016-06-23 2017-06-19 钟表的轮系机构
JP2018524089A JP6876694B2 (ja) 2016-06-23 2017-06-19 時計の輪列機構

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JP2016-124837 2016-06-23

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WO2017221522A1 (fr) 2016-06-23 2017-12-28 シチズン時計株式会社 Mécanisme d'engrenage pour horloge

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JP2002227967A (ja) * 2001-02-01 2002-08-14 Seiko Epson Corp 歯車、この歯車を備えた動力伝達装置、この動力伝達装置を備えた機器および歯車の製造方法
JP2012102877A (ja) * 2010-11-11 2012-05-31 Eta Sa Manufacture Horlogere Suisse 一定のトルクを有するプロフィールギヤ

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CN109154793A (zh) 2019-01-04
CN109154793B (zh) 2020-08-14
EP3447589B1 (fr) 2022-04-27
US20190163136A1 (en) 2019-05-30
WO2017221897A1 (fr) 2017-12-28
EP3447589A1 (fr) 2019-02-27
US10895844B2 (en) 2021-01-19
JPWO2017221897A1 (ja) 2019-04-11
JP6876694B2 (ja) 2021-05-26

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